DE2620570C3 - Single helical gear planetary gear with load compensation - Google Patents

Description

a) the planetary gear carrier (5) is mounted in a radial bearing (11) in the case of a large clamping length (L) of the bearing pin (4) and via the meshing of the planetary gears (3) in the outer central gear (6) in the housing (1),

b) the end faces of the planet gears (3) are designed as a plane surface perpendicular to their central axis and that of the pressure rings (9, 10). starting from a flat surface. crowned.

2. Single helical spur gears planetary gear according to claim I. with more than three planet gears, characterized in that the outer central wheel (6) is designed as an elastically deformable ring is.

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From US PS 32 06 993 a planetary gear is known according to the features of the preamble. Here, pressure ranges are used. turns, one of which is conical and another, from a conical surface starting out, has a convex (- iche this training is an integral part in every company case punctual contact obtained.

Furthermore, planetary gears are known to which bet radial load balancing two of the main links, e.g. B. the inner central gear and the planet carrier radially are movable (DE-PS 6 06 634). Single helical spur planetary gears are also known with radial and axial load compensation, in which the compensation of the axial tooth forces by pressure drops The touching surfaces of the pressures and the planetary gears are conical surfaces with formed small angles of inclination (DE-PS 11 65 37O.DEPS21 10 252. DE-AS 12 40 712).

It is also known to single-line the bearing pins of the planetary gears in the planetary gear carrier to be held clamped as a self-supporting part (DF. PS 4 24 4 5 3. DE-PS 5 03 307. DEPS 15 00 451). Trained in this way te planetary gears have the disadvantage, however, that the tooth forces support the bearing boom fastened as a free carrier! Deform zen more elastically compared to the two-sided fastening. The planetary gear thus leads a Swivel movement off. which leads to corner wear of the toothing and thus to a risk to the Transmission leads. To overcome this disadvantage it is known to store the planetary gear on a sleeve, to fasten this on one side at the end of a flexible bolt and rigidly with this bolt as a cantilever beam to connect the planet carrier (DE-PS 15 00 451). However, this measure requires a high structural effort and downsized also nights! ' obviously with the same bearing diameter thereby even more deforming bearing bolts.

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55 In the case of a planetary gear set according to the preamble of claim 1 (DE-PS 21 10 252), the radial load compensation takes place by means of radially movable central gears with a planetary gear carrier mounted on both sides. The contact surfaces on the pressure rings and on the planetary gears are conical, so that dimensional deviations are unavoidable in the width of the planetary gears. These manufacturing-related width deviations are compensated for by the radial mobility of the pressure rings, thus enabling axial load compensation. This training as well as the articulated mounting of the outer central wheel and also the mounting of the planetary gear carrier on both sides cause high construction costs.

The object of the present invention, on the other hand, is as simple as possible while maintaining a good radial and axial load balance To achieve transmission structure.

The solution according to the invention leads to a very simple design of the transmission, since the storage of the planetary gear carrier takes place only in a radial bearing, the outer central gear with the simplest means is held firmly in the housing and the flat surfaces on the Planet gears are easy to manufacture if the widths of the planet gears are strictly adhered to. aside from that reach the flat surfaces that the toothing of the planetary gears along the tooth width evenly wearing.

According to a further feature of the invention, a spur planetary gear with more than three Planetary gears, the outer central gear be designed as an elastically deformable ring (DE-PS 21 10 252). This also compensates for manufacturing errors that could jeopardize the desired load balancing.

It is known per se, one-sided to planet carrier. to store. It is still using a planetary gear Load balancing known in which the contact surfaces the pressure rings and the planet gears can be pian (GB-PS 8 04 223). Furthermore it is at Bekanni tapered roller bearings that plan Kejelrolien Provide end faces that run against a conical counter surface (DFPS 5 32 999)

The invention is based on one in the Drawing illustrated embodiment described in more detail. In the drawing / eigt

Fig. 1 is a spur planetary gear with fixed hanging outer central wheel in longitudinal section

F ι g 2 the formation of the contact surface on one Pressure of the outer or inner central wheel

Fig. 3 a schematic representation of the Beruh rungshnie between / white conventional thin rings with conical contact surfaces

Fig. 4 see a view of the representation of the mountain rungshnie / vuschen / white pressure rings with plan and spherical contact surfaces according to the invention.

Fig. 5 an apparent representation of the bolt connection formation and the expansion of the Rohnings

In the exemplary embodiment according to Fig. ' .1 ¹ Ie parts of the spur gears pinnet gear are arranged in cnem Ge ^ ι se 1 This spur gears P'cietengetri ·· ·:

consists essentially of an inner gear wheel I, a number of planet gears 3, which are rotatably mounted on bolts 4 of the planet gear carrier 5, and an outer central gear 6.

The bearing pins 4 are on one side on a ratio ' moderately large length Lim planetary gear carrier 5 attached. The inner one, in the planet gears 3 only through

The central gear 2, which is held radially in mesh with the teeth, is connected to a hub 7 via a double, straight-toothed tooth coupling 8 radially and axially movably connected.

The outer central wheel 6 is rigidly attached to the housing 1 via a thin-walled intermediate piece 16 equipped with bores 17 and centered directly in this via a centering Z. In addition, the part of the central wheel 6 carrying the toothing is dimensioned in such a way that an elastic deformation of the desired size occurs under the action of the tooth forces

To compensate for the axial tensile forces, there are pressure rings 9 and 10 on both sides of the central gears 2 and 6 of the teeth arranged- The contacting surfaces of the pressure rings 9 and 10 and the planetary gears 3 are plane surfaces.

In addition, the annular flat surfaces of the pressure rings 9 and 10 are given a convex contour over the Ring height, as shown in FIG. 2.

The storage of the planetary gear carrier 5 takes place in a bearing 11 and the gear meshes in the rigid Outer central wheel 6 fastened to the housing 1.

The manufacturing errors with more than three planet gears, which endanger the load balancing, are caused by the radially elastically deformable, outer Zer.ii-alrad 6 balanced. The double tooth clutch 8 is also the same as that outside of the gearbox possible errors, such as alignment errors, errors from thermal expansion or foundation deformations.

The direct centering of the outer center wheel 6 in the housing 1 reduces the manufacturing-related eccentricity errors between the axis of the outer Central wheel 6 and the axis of the planetary gear carrier 5.

The creation of flat surfaces on the planet gears 3 as pressure ring contact surfaces ensures the axial load balancing through the resulting possibility of having one on all planetary gears at the same time Gear to carry out the surface grinding of these surfaces, which endangers the load balancing Differences in width of the planetary gears are avoided.

The attachment of the bearing pin 4 as a cantilever enables the construction of a very simple one Planetary gear carrier 5. This type of fastening can, however, * 5 lead to the tangential / anticipatory forces Bend the bearing pin = n 4 more than with the mutual fastening, so that the gears due to the inclination of the planet gears 3 could come into play unevenly along the face width. To avoid this effect the contact surfaces of the pressure rings 9 and 10 and the planetary gears 3 are designed as flat surfaces. In addition, the contact surfaces of the pressure rings 9 and 10 according to K 1 g. 2 one for better oil film formation convex contour.

In Fig.3 is the conventional, slightly conical Formation of the contact surfaces shown, in which the pressure ring 9 and planet gear 3 theoretically run along touch line 12. This line 12 runs parallel to the pivot axis of the planetary gear 3 when this as The result of the deformation of the bearing pin 4 is inclined.

In the embodiment according to the invention according to FIG. 4 there is also a line contact, however with the difference that the line 13 in the circumferential direction, that is perpendicular to the pivot axis of the planetary gear 3, This ensures that the resulting from the axial force compensation and runs along the line 13 acting support forces prevent a tilting device of the planet gear 3. This z. B. by the Thrust ring 9 reached leadership defect of the planetary gears 3 is still enlarged by the diagonal opposite second support of the planetary gear 3 with the pressure ring 10 according to Fig. 1. The Support on this second part is particularly effective because the ring in ring means that the Area coverage a greater length of line 13 as a result of the support with the pressure ring 9. The guiding effect achieved prevents somi < inclination of the planetary gears, so that an even load without prejudice to 3pin deformation the tooth flanks come about across the face width.

The formation of the contact surfaces also reduces the surface pressure, since the contact length is considerable is larger than in the previous tapered training.

An intensive lubrication is in the pressure rings 9 (Fig. 1) by the radial bores 14 and the Storage space 15 reached. In this way, the oil is supplied from the inside of the using the centrifugal force Central wheel 2 and an even distribution along the circumference of the pressure ring through the storage space 15. The convex contour of the pressure rings 9 and 10 creates an inside in the direction of the flowing oil narrowing gap which supports the formation of the lubricating film.

The extremely large clamping length L of the bearing pin 4 ir .. planetary gear carrier 5 ensures an absolutely secure fastening which is required with regard to the pin deformation.

For the operational safety of the planet wheel bearing, it is important to avoid edge checking at the end of the bearing. In Fig. 5 it is shown how this is possible by conical expansion of the planetary gear bore. Without this measure there could be an undesirable edge pressure at the point K / u if, when the bearing pin 4 bends, the planet gear i is kept approximately parallel to the operating axis due to the guiding effect of the pressure rings.

For this purpose 2 sheets of drawings

Claims (1)

Patent claims: 1.Single helical toothed spur gears planetary gear, with a few planetary gear carriers with planetary gears on bearing bolts, with an inner zeniral gear and an outer central wheel, firmly connected to the housing, with pressure rings on both sides for axial load balancing, with the inner central wheel and another of the three main links for radial load compensation are radially movable, characterized by the combination of the following Characteristics: